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WO2019011951A1 - Procédé et dispositif d'expansion d'un gaz avec un moteur à pistons alternatifs - Google Patents

Procédé et dispositif d'expansion d'un gaz avec un moteur à pistons alternatifs Download PDF

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Publication number
WO2019011951A1
WO2019011951A1 PCT/EP2018/068724 EP2018068724W WO2019011951A1 WO 2019011951 A1 WO2019011951 A1 WO 2019011951A1 EP 2018068724 W EP2018068724 W EP 2018068724W WO 2019011951 A1 WO2019011951 A1 WO 2019011951A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
gas
dead center
working space
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2018/068724
Other languages
German (de)
English (en)
Inventor
Alexandre Voser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Burckhardt Compression AG
Original Assignee
Burckhardt Compression AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Burckhardt Compression AG filed Critical Burckhardt Compression AG
Publication of WO2019011951A1 publication Critical patent/WO2019011951A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B25/00—Regulating, controlling or safety means
    • F01B25/02—Regulating or controlling by varying working-fluid admission or exhaust, e.g. by varying pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/06—Rotary or oscillatory slide valve-gear or valve arrangements with disc type valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/04—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members
    • F16K3/06—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages
    • F16K3/08—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages with circular plates rotatable around their centres
    • F16K3/085—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages with circular plates rotatable around their centres the axis of supply passage and the axis of discharge passage being coaxial and parallel to the axis of rotation of the plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C21/00—Oscillating-piston pumps specially adapted for elastic fluids

Definitions

  • the invention relates to a method and a device for
  • the object is achieved in particular with a method for
  • Compressed gas into the working space and a controllable second valve comprises by the first valve is closed, a residual gas in the working space is compressed and then the first valve is opened by the compressed gas flows when the first valve is open in the working space and the first valve is then closed by the gas in the working space is relieved by the
  • Dead center of the reciprocating engine is closed, so that after the closing of the second valve located in the working space residual amount of gas is compressed.
  • the object is also achieved, in particular, a method for releasing a pressurized gas under a gas pressure with a
  • Reciprocating piston engine the reciprocating piston engine a reciprocating piston, a limited by the movable piston working space, a controllable first valve for supplying the
  • Compressed gas into the working space and a controllable second valve for discharging gas from the working space comprises by the closed first valve, the piston to a top dead center is moved, and the second valve is closed before reaching top dead center, whereby a residual gas in the working space is compressed by the piston by the first valve is opened by the compressed gas flows when the first valve is open in the working space, the piston to a lower Dead center is moved, the first valve is closed during the movement of the piston, and the gas in the working space is expanded by the second valve is opened by the expanded gas through the second valve and by the top dead center moving Piston is ejected from the working space, and by the second valve is closed, before the piston has reached the top dead center, so that after closing the second valve in the working space located gas remaining amount is compressed, and thereby in the top dead center above the the first valve applied pressure difference is reduced.
  • a device for relaxing a compressed gas comprising a reciprocating piston engine, wherein the reciprocating engine comprises a reciprocating piston and a limited by the movable piston working space, and comprising a controllable first valve, and comprising a drive device for driving the the first valve, wherein the pressurized gas is supplied via the first valve to the working space, and wherein the pressure gas located in the working space can be relaxed in the working space.
  • the erfmdungsgemtreu method allows a relaxation of a compressed gas or a compressed gas from a higher pressure level to a lower pressure level using a reciprocating engine, so that the reciprocating engine, which is usually operated as a reciprocating compressor, as
  • Hubkolbenexpander is operable.
  • the erfmdungsgemässe method makes it possible to operate a previously operated only as a reciprocating compressor reciprocating engine as Hubkolbenexpander.
  • the erfmdungsgemässe method for operating the reciprocating engine, or the erfmdungsstructuree reciprocating engine comprises a controllable first valve for controlled supply of the pressurized gas pressure in the working space of the reciprocating engine. The supplied compressed gas is then expanded in the working space, and the expanded gas is then at least partially from the
  • Pressurized valves such as those used for reciprocating engines or for reciprocating compressors, can usually either not open at all, or, if they can be opened, only by using large forces and with correspondingly high wear.
  • the erfmdungsgemässe method allows a relaxation of the compressed gas with a
  • Reciprocating piston by the compressed gas is supplied via the first valve to the working space of the reciprocating engine by the
  • supplied compressed gas is subsequently expanded in the working space to a bottom dead center and then partially over a
  • controllable second valve is ejected from the working space, and then by the second valve is closed and a remaining in the working space of the reciprocating engine residual gas is compressed such that the voltage applied to the first valve
  • Reciprocating engine is reduced, preferably such that the pressure difference across the first valve when opening the first valve is substantially differential pressure.
  • This makes it possible to open the first valve in the region of the top dead center of the reciprocating engine, so that the compressed gas can flow into the working space of the reciprocating engine, then expanded in the working space, and then ejected from the working space.
  • the first valve is also opened low wear.
  • the invention has the advantage that the reciprocating engine, which could previously be operated in particular only as a reciprocating compressor, now also as Hubkolbenexpander is operable. Another advantage is the fact that the first valve can be opened controllable despite the applied pressure of the compressed gas.
  • the forces required to open the first valve are not all that high, so that the first valve can be opened in particular in a very precisely timed manner.
  • the second valve is actuated in such a way that the residual amount of gas remaining in the working chamber of the reciprocating piston is determined so that the residual amount of gas in the working space in the region of top dead center has a pressure which is higher than the pressure of the compressed gas has that the first valve can be operated very easily.
  • the first valve is also designed as an automatic valve, that its closing element lifts off the valve seat when the pressure in the working space is higher than the pressure of the compressed gas.
  • the closing element is no longer on the valve seat when opening, which allows a particularly easy and also a frictionless or largely frictionless opening of the closing element.
  • the first valve is advantageously designed as a rotary valve, so that the closing element when opening, after lifting, rotated, preferably can be rotated without friction.
  • the energy released during the expansion of the compressed gas in the interior of the cylinder or the energy released during the expansion of the compressed gas to the reciprocating piston or the piston energy is used and dissipated, for example by the reciprocating engine drives an electric generator via a shaft driven by pistons to get electrical energy
  • Reciprocating compressor or operated as Hubkolbenexpander so that either a gas is compressed to a compressed gas, or that a pressurized gas pressure is expanded, with a corresponding control of the reciprocating engine or its valves, the reciprocating engine either compresses the gas or the compressed gas expands.
  • a reciprocating engine is for example suitable for loading and unloading a gas storage.
  • both the first valve and the second valve are designed as slide valves, advantageously as linearly movable slide valves, and particularly advantageously as rotatably movable rotary slide valves.
  • the first valve could be designed as a slide valve
  • the second valve comprises a lift-off gripper, for controllably closing the second valve.
  • the reciprocating engine can also be operated in a part-load operation by only a subset of the maximum possible amount of gas expands and / or compressed in the working space.
  • the reciprocating engine is designed as a double-acting reciprocating engine comprising two counteracting working spaces.
  • the double-acting reciprocating engine is operated such that the first working space is used as an expansion space to relax a compressed gas, and that the second working space is used as a compression space to compress a gas.
  • both the first and the second working space each comprise a controllable first and a controllable second valve.
  • a reciprocating compressor may comprise both cylinders in which a
  • the reciprocating compressor comprises a common
  • associated pistons are connected to the crankshaft, so that the piston when compressing the gas draw energy from the crankshaft, and so that the pistons release energy to the crankshaft during expansion of the gas.
  • Fig. La schematically a reciprocating piston engine with a piston in the position of bottom dead center;
  • Fig. Lb schematically shows a reciprocating engine with the piston in the
  • Fig. 2 shows schematically a reciprocating engine with a double-acting
  • Fig. 3 is a P-V diagram of a reciprocating engine during a
  • Fig. 4 is a P-V diagram of a reciprocating engine during a
  • Fig. 5 is a P-V diagram of the reciprocating engine during a first variant of a partial load expansion operation
  • Fig. 6 is a P-V diagram of the reciprocating engine during a second
  • Fig. 9 is a perspective view of a valve seat
  • FIG. 10 is a perspective view of a closing element
  • Fig. 1 1 shows a longitudinal section through a valve closure
  • FIG. 12 shows a valve closure in the raised closed position
  • FIG. 13 shows a valve closure in the raised open position
  • Fig. 14 is a P-V diagram of the reciprocating engine during a third variant of a partial load expansion operation
  • Fig. 15 shows a further embodiment of a reciprocating piston engine with valves
  • Fig. 16 is a reciprocating engine comprising four pistons
  • Fig. 17 shows schematically an arrangement for processing a fluid. Basically, the same parts are provided with the same reference numerals in the drawing figures.
  • Figure la shows a reciprocating engine 2 comprising a cylinder 3 and a reciprocating piston 4 therein, wherein the cylinder 3 and the piston 4 define an interior space 5, the interior 5 via a first valve 6 and a line 2 1 with a Pressure vessel 9 is connected, and wherein the inner space 5 via a second valve 7 and a conduit 2 1 fluid conduct with a space 20, for example an outer space such as the atmosphere is connected to pressure PA, which has a lower pressure than the gas pressure PD of the gas GD in
  • Pressure vessel 9 The piston 4 is connected via a piston rod 8 with a drive, not shown.
  • Figure l a shows the piston 4 in the position of a bottom dead center Pi, ie with the largest possible interior space 5, comprising a volume VUTP.
  • the cylinder 3 has at its end face channels 3a, 3b, which are fluidly connected to the valves 6, 7.
  • the first valve 6 is designed as a pressure valve 6c
  • the second valve 7 is designed as a suction valve 7c.
  • the pressure valve 6c and the suction valve 7c are only schematically using one
  • Reciprocating compressor or operated as Hubkolbenexpander.
  • the pressure valve 6c and the suction valve 7c could be operated automatically, for example by the linear drive 15
  • Suction valve 7c controlled via the drive 15 shown schematically open or closed.
  • the drives 15 effect a linear movement of the pressure valve 6 c or of the suction valve 7 c, in order in each case to lift a closing element from a valve seat or to press it against it.
  • Figure lb shows a reciprocating engine 2 with a position of the piston 4 at top dead center P3, that is the smallest possible interior space 5, comprising a volume VOTP. That still at top dead center P3
  • VOTP of the interior 5 is usually referred to as dead space, dead space or residual gas.
  • FIG. lb shows the first valve 6 and the second valve 7, each with a valve seat 12 and a rotatably arranged closing element 13.
  • FIG. 7 to 13 are details of an embodiment of such
  • FIG. 2 shows a reciprocating piston engine 2 with a double-acting piston 4 in that it divides the interior 5 into a first interior 5a and a second interior 5b.
  • Each interior 5a, 5b is connected via a corresponding first valve 6, 6a, 6b and a corresponding second valve 7, 7a, 7b and via fluid lines 21 fluid connected with not shown in detail rooms.
  • the valves are 6,7
  • a rotary slide valve preferably configured as a rotary slide valve.
  • the first valve 6 is operated as an intake valve and the second valve 7 operates as an exhaust valve, so the point P2 is referred to as the second valve closing angle P2 or the exhaust valve closing angle P2, and the point P 4 is referred to as the first valve closing angle P 4 or as the intake valve closing angle P 4 ,
  • the abscissa V shows the size of the inner volume of the inner space 5, wherein in particular the lower dead center volume VUTP at bottom dead center Pi, and the top dead center volume VOTP at top dead center P3 is shown.
  • the ordinate P shows the pressure of the gas in the interior space 5.
  • Diagram includes the points Pi, Po, P3 and P 4 , or the line connecting these points, or this
  • the first valve 6 is preferably opened at top dead center P3, so that the pressurized in the pressure vessel 9
  • Compressed gas GD flows into the interior 5 and the piston 4 is displaced along the line P34 to the point P 4 , from which point P 4 the first valve 6 is controlled, and preferably positively controlled closed.
  • the piston 4 continues to move to the right, so that the gas located in the interior 5 along the line P 4 i to the bottom
  • Dead center Pi is relaxed, in which the second valve 7 is controlled open, for example, to the atmospheric pressure PA out.
  • the piston 4 then moves with the second valve 7 open to the left to the point Po, at which the second valve 7 is closed controllable.
  • the cycle follows the line P03, wherein at point P3 the first valve 6 is forcibly opened, that is, forcibly positively opened, so that the compressed gas GD flows into the interior 5 as already described.
  • the term positively controlled is understood to mean that the valve without support by the across the valve applied differential pressure, that is at any pressure difference, through Forced by a drive mechanical forces is forcibly opened or closed.
  • a disadvantage of this first P-V diagram is that when opening the first valve 6, a large pressure difference across the first valve 6 is applied, since the gas pressure in the interior 5 shortly before the opening of the first valve 6 corresponds approximately to the atmospheric pressure PA.
  • the first valve 6 can be due to the applied pressure difference only very difficult to open, possibly only with considerable effort. If the drive 15 generates a sufficiently large force, so the first valve 6 can thus be opened positively controlled, but this has the disadvantage that when opening the first valve 6, a significant wear occurs.
  • the positively controlled opening of the first valve 6 has the further disadvantage that the gas pressure in the interior 5 can be relatively deep, so that the energy of the gas flowing into the interior 5 in the valve is destroyed in the valve as a valve loss.
  • the gas pressure in the interior 5 can be relatively deep, so that the energy of the gas flowing into the interior 5 in the valve is destroyed in the valve as a valve loss.
  • Diagram shows a cycle or a method comprising the points Pi, P2, P3 and P 4 .
  • a process for relaxing the compressed gas located in the pressure vessel 9 GD takes place in that the second valve 7 already before reaching the top dead center P3, namely the second
  • Valve closing angle P2 is closed, so that at point P2 is still a residual amount of gas GR or a residual gas volume VR under the pressure PA in the working space 5.
  • a reciprocating engine has a dead volume, also referred to as dead space, so that, for example, when the piston is in the position of top dead center P3, still a top dead center volume VOTP in dead spaces such as the cylinder interior and in the fluid with the cylinder interior conductive connected valves is present.
  • Gas residual volume VR comprises the pressure at relaxation pressure PA, the amount of gas in the dead center volume VOTP and also includes a
  • the weight of the remaining gas amount GR is maintained during the compression from the depressurization pressure PA to the gas pressure at the top dead center P3, whereas the volume of the remaining gas amount GR at the top dead center P3 corresponds to the dead center volume VOTP.
  • the weight of the gas remaining amount GR is maintained, whereas the gas remaining amount volume VR existing at the point P2 under the pressure PA is reduced due to the increasing pressure.
  • Gas residual volume VR includes pressure PA as in FIG. 3
  • Additional volume Vz corresponds to an additional gas quantity, wherein the weight of the additional gas quantity or the weight of the gas remaining quantity GR remains constant during compression from point P2 to P3, while the residual gas volume VR of the residual gas quantity GR at top dead center P3 is reduced to the volume VOTP.
  • Gas residual quantity GR has the consequence that at the top dead center P3, the pressure difference across the first valve 6 is reduced.
  • the first valve 6 is preferably opened controlled in the region of the top dead center P3, so that the compressed gas GD flows into the working chamber 5 when the first valve 6 is open, with the piston 4 moving back towards the bottom dead center after reaching top dead center, that is, in the illustration according to FIG. 3, moved to the right.
  • the first valve 6 is then closed controlled again at the first valve closing angle P 4 , and the gas located in the working space 5 along the curve P 4 i relaxed until the second valve 7 is opened in the region of bottom dead center Pi.
  • the piston 4 moves back to the top dead center, in the illustration according to Figure 3 to the left, wherein the gas in the working chamber 5 is ejected as long as the second valve 7 until the second valve 7 closed again controlled at the second valve closing angle P2 becomes.
  • range means a crankshaft angle range of + / - one given angle, for example +/- 10 ° and preferably +/- 5 ° to understand, with respect to the top dead center P3 and the bottom dead center Pi.
  • the erfmdungsgemässe method thus does not require that the first and second valve 6,7 exactly at It is sufficient if the first or the second valve 6, 7 is opened in the area of these dead centers, for example in a range +/- 5 ° about this
  • the crankshaft angle is predetermined by the rotation of the drive of the reciprocating engine 2, wherein the top dead center P3 of the piston 4 corresponds to a crankshaft angle of 0 ° or 360 ° and the bottom dead center Pi of the piston 4 corresponds to a crankshaft angle of 180 °. Since the first valve 6 and the second valve 7 are preferably opened and closed under control of the drive means 15, the effective angle at which the valve 6, 7 is opened or closed can be determined by the drive device 100
  • first valve. 6 shortly before reaching the top dead center P3, open at top dead center P3, or shortly after reaching the top dead center P3 open, or it may prove advantageous the second valve 7 shortly before reaching the bottom dead center Pi, at bottom dead center Pi , or shortly after reaching bottom dead center Pi controlled open.
  • the first valve 6 and the second valve 7 are preferably as
  • Rotary slide valves 10 configured, wherein the rotary valve 10 controlled by a rotation of a closing element 13 can be opened and controlled closed.
  • a controllable first valve 6 is shown in Figure 7, and an embodiment of a controllable second valve 7 in Figure 8.
  • the pressure in the interior 5 at top dead center P3, and thus the opening when the first valve 6 over this applied pressure difference, is determined by the volume and the pressure of the residual gas quantity GR at the point P2, at which the second valve 7 is closed, and by the subsequent compression, caused by the movement of the piston 4 from the point P2 to the top dead center P3.
  • Working gas 5 is relaxed by the expanded gas is discharged via the second valve 7 from the working space 5, and the second valve 7 is closed before reaching a top dead center P3 of the reciprocating engine 2, so that after closing the second Valve 7 located in the working space 5
  • Gas residual quantity GR is compressed.
  • the second valve 7 is in the region of the lower
  • Valve closing angle P2 is closed, in which the
  • Gas residual quantity GR is located in the working space 5, wherein the residual gas quantity GR is subsequently compressed in the working space 5, wherein in the region of the top dead center P3 on the closed, first valve 6 applied differential pressure DD by at least one of the second parameters
  • Valve closing angle P2 and residual gas quantity GR is determined. Immediately after opening the first valve 6 in the region of the top dead center P3, this differential pressure DD is applied to the first valve 6, wherein this
  • Differential pressure DD is changed by the subsequently flowing into the working space 5 compressed gas GD.
  • the second valve closing angle P2 is advantageously set in such a way that the residual gas quantity GR in the region of the top dead center P3 essentially has the pressure PD of the compressed gas GD, so that the first valve 6 can be opened in the region of the top dead center P3 essentially without differential pressure or completely without differential pressure.
  • the residual gas quantity GR or the second valve closing angle P2 is selected such that the working space 5 in the region of the top dead center P3 a
  • the first valve 6 after the top dead center P3 at a first valve closing angle P 4th
  • Working space 5 is located, wherein the gas expansion amount GE subsequently is relaxed in the working space 5, so that the gas in the region of the bottom dead center Pi has a pressure relaxation gas PE, wherein the pressure applied at closed second valve 7 in the region of bottom dead center Pi in the working space 5 expansion gas pressure PE by at least one of the parameters first valve closing angle P 4 and
  • Gas expansion amount GE is determined.
  • Valve closing angle P 4 is set such that the
  • Gasexpansionsmenge GE in the region of the bottom dead center Pi has a pressure relaxation gas ⁇ , which essentially the
  • adjacent outlet pressure PA of the second valve 7 corresponds to the atmospheric pressure, so that the voltage applied to the second valve 7 pressure difference is minimized, and the second valve 7 is advantageously opened substantially differential pressure.
  • Valve closing angle P ' 2 selected such that the gas remaining amount GR in the working chamber 5 in the region of top dead center P'3 with closed first valve 6, a gas pressure p ma x, which exceeds the gas pressure PD of the compressed gas GD.
  • Valve closing angle P ' 4 is selected such that when the second valve 7 is closed, the gas expansion amount GE in the region of the bottom dead center P'i has a pressure relaxation gas ⁇ , which is smaller than that
  • the first valve 6 and / or the second valve 7 comprises a valve seat 12 with a passage opening 12a and a Closing element 13 for closing the passage opening 12a, wherein the closing element 13 of the first valve 6 in the region of top dead center P3 due to the gas pressure of the gas rest quantity GR is automatically raised relative to the valve seat 12 and / or that the closing element 13 of the second valve 7 in the region bottom dead center Pi due to the gas pressure of the gas expansion amount GE automatically with respect to
  • Valve seat 12 is raised. This automatic lifting is not yet referred to as opening the valve, since the closing element 13 is raised only slightly, preferably in the region of less than one millimeter, and thus, if any, only a negligible gas flow through the valve takes place.
  • the closing element 13 of the first and / or the second valve 6, 7 is after the
  • the closing element 13 is preferably by a
  • first valve 6 and / or the second valve 7 comprise a valve seat 12 with a passage opening 12a and a
  • Closing element 13 for closing the passage opening 12a wherein the first valve 6 and / or the second valve 7 is designed as a rotary valve, and wherein the passage opening 12a is opened or closed by a rotation of the closing element 13.
  • first and / or second valve 6, 7 may also be designed such that the
  • Closing element 13 is not perpendicular to the valve seat 12 is movable so that no automatic lifting of the closing element 13 is possible.
  • the closing element 13 is coupled to a drive 15, which is strong enough to the closing element 13 of the open positively controlled by the first valve 6 and the second valve 7 and positively closed to close.
  • Specified process parameter setpoint Vs of the first valve 6 for example, the pressure in the interior 5 in the region of the upper
  • an exhaust valve closing angle actual value P21 of the second valve 7 is varied during successive stroke cycles and a process parameter actual value Vi of the first valve 6 is measured depending on the exhaust valve closing angle actual value P21
  • Exhaust valve closing angle actual value P21 is determined as the exhaust valve target closing angle P2S011 at which the process parameter actual value Vi is closest to the process parameter set value Vs.
  • the second valve 7 is then actuatable at the outlet valve target closing angle P2S0I1
  • the pressure occurring in the interior 5 can be predetermined or adjusted in the region of the top dead center P3.
  • This method can also be used in an analogous manner to specify a method parameter setpoint value Vs of the second valve 7, for example the pressure in the interior space 5 im
  • the compressed gas GD is expanded via at least two reciprocating piston engines 2 connected in series, by the pressurized gas GD under pressure PD in a first
  • Reciprocating piston is relaxed to a first flash gas pressure PEI, and by the under the flash gas pressure
  • PEI standing gas is relaxed in a subsequent, second reciprocating engine to a second expansion gas pressure PE2.
  • FIG. 4 shows a per se known PV diagram or a cyclic process of a reciprocating piston engine 2 during a process Compression operation.
  • a piston starting from the point Q l, the bottom dead center, to the point Q3, the top dead center moves, with an aspirated, located in the working space 5 gas
  • Working space 5 is ejected.
  • the piston starting from the point Q3 to the point Q 1, the bottom dead center moves.
  • the first valve 6 is closed and the second valve 7 is opened at point Q4, wherein from point Q4 to point Q L, a gas is sucked into the working space 5 via the second valve 7, thereby filling the working space 5 with gas becomes.
  • the second valve 7 is closed and the gas in the working space 5 is compressed.
  • the reciprocating engine 2 can be operated in two different operating modes, namely as a reciprocating compressor or reciprocating expander, which can be switched controllably between these operating modes, in particular by the first and the second valve 6,7 are opened and closed controllable according to the selected operating mode ,
  • a reciprocating compressor or reciprocating expander which can be switched controllably between these operating modes, in particular by the first and the second valve 6,7 are opened and closed controllable according to the selected operating mode .
  • Method for relaxing and compressing a gas G with the reciprocating engine 2 is such that the gas with the
  • Reciprocating piston machine 2 is compressed to the pressurized gas DG under pressure PD, and / or that under pressure PD standing pressure gas GD is relaxed again.
  • the reciprocating engine 2 is operated continuously such that the reciprocating engine 2 is operated during continuous operation by a corresponding control of the first valve 6 and the second valve 7 as a Hubkolbenexpander or a reciprocating compressor, with a corresponding control of the valves preferably during a continuous
  • FIG. 5 shows in a PV diagram a further, advantageous method in which the amount of gas expanded by the reciprocating piston expander 2 can be influenced by means of a partial load control.
  • the first valve 6 is prematurely closed at a first valve closing angle P 4, in which a partial gas volume VTE or a partial gas expansion amount GTE is located in the working space 5.
  • Partial gas expansion quantity GTE is smaller than the maximum gas expansion quantity GEMAX possible at point P4.
  • the Operagasexpansionsmenge GTE is then expanded until the second valve 7 is opened at the operating point P'l. Thus, only a subset of the maximum possible amount of gas is expanded.
  • FIG. 6 shows in a P-V diagram a further, advantageous method in which the amount of gas expanded by the reciprocating piston expander 2 can be influenced by means of a partial load control.
  • the second valve 7 is closed prematurely at a second valve closing angle P'2, in which there is an excess gas volume VRZ or an excess gas quantity GRZ in the working space 5.
  • the gas pressure in the working chamber 5 exceeds the pressure PD in the pressure vessel 9 already at the point P3 ', so that the first valve 6 can be opened, and preferably automatically or positively opened, and the excess gas quantity GRZ pressed into the pressure vessel 9 for the time being is, before, after the top dead center P3, gas can flow through the first valve 6 in the working space 5 again.
  • Reciprocating piston engine 2 as shown in Figure 2, a double-acting piston 4, which divides the inner space 5 in a first inner space 5a and a second inner space 5b, each interior 5a, 5b a first valve 6 and a second valve 7 is assigned, and so that simultaneously in the first inner space 5a the gas is compressed to the compressed gas GD and in the second inner space 5b, the compressed gas GD is relaxed. In addition, different gases could be promoted.
  • a partial load control such as with the figures 5 and 6
  • FIGS. 7 to 13 show exemplary embodiments of suitable valves and their components for carrying out the method according to the invention.
  • FIG. 7 shows in a longitudinal section a first valve 6 comprising a valve seat 12 with passage openings 12a, end face 12b and bore 12e, and comprising a closing element 13 rotatable about a rotation axis D for opening and closing the passage openings 12a.
  • the valve seat 12 and the closing element 13 form a
  • the first valve 6 also includes a lantern 16 with passage openings 16a, and includes a drive 15 for rotating a shaft 14, which may be directly connected to the closing element 13 in order to drive this.
  • the shaft comprises a first shaft part 14a, a longitudinally L elastic coupling 19 and a second shaft part 14b.
  • the second shaft part 14b is guided in the bore 12e and is movable in the longitudinal direction L.
  • This embodiment has the advantage that the closing element 13 can automatically lift off from the valve seat 12 under appropriate pressure conditions or can automatically rest against the valve seat 12.
  • a sensor 100c measures the distance to the second shaft part 14b, from which the drive device 100 the distance between
  • Locking element 13 and end face 12b of the valve seat 12 can determine.
  • the drive device 100 is connected via the line 100b with the
  • Sensor 100c via the line 100a with the actuator 15, and via the line lOOd with a sensor lOOe, for example a Rotary angle sensor of the crankshaft of the reciprocating engine connected.
  • a sensor lOOe for example a Rotary angle sensor of the crankshaft of the reciprocating engine connected.
  • process parameters such as gas pressure PD or flash gas pressure PE, or which control, for example, first or second valves 6,7.
  • FIG. 8 shows in a longitudinal section a second valve 7, which is designed to be similar to the first valve 6 according to FIG. 7, with the difference that the closing element 13 is arranged on the opposite side of the valve seat 12.
  • the shaft 14 extends continuously through the valve seat 12.
  • the shaft 14 includes a recess 14d, in which a sensor 18 is arranged, and a longitudinally elastic coupling L 19, so that the closing element 13 is movably mounted in the longitudinal direction L, wherein the Clutch 19 is preferably rigid with respect to a rotation about the axis of rotation D.
  • the sensor 18 for example, the change in the distance between the first and the second shaft part 14a, 14b or the position of the closing element 13 with respect to the valve seat 12 can be measured.
  • FIG. 9 shows the valve seat 12 in detail. This comprises a plurality of passage openings 12a and webs 12f, and includes an end face 12b, an annular bearing surface 12c and the bore 12e with
  • FIG. 10 shows the closing element 13 in detail. This comprises a plurality of closing arms 13a and intermediate spaces 13b, and comprises a hub 13e and a central bore 13c.
  • Figure 1 1 shows a longitudinal section that shown in Figure 7
  • Rotary slide valve 10 in detail. 9 shows a longitudinal section through the valve seat 12 according to FIG. 9 and a longitudinal section through the closing element 13 according to FIG. 10.
  • the closing element 13, having a sealing surface 13d, is raised relative to the valve seat 12, forming a gap S.
  • the closing element 13 assumes this position in the case of the first valve 6 shown in FIG. 7 when the closing element 13 has been automatically raised due to the pressure conditions applied to the closing element 13.
  • FIG. 12 shows the rotary valve 10 in this position from a perspective view.
  • the section along the line A-A is also shown in Figure 11. This position is not yet referred to as open because the
  • FIG. 13 shows the closing element 13 raised in relation to the valve seat 12 in the completely open position, in that the closing element 13 has been rotated in the direction of rotation D 1 in relation to the position according to FIG. 12, and the passage opening 12a is no longer covered and thus completely opened.
  • the closing element 13 is rotated in the lifted position to
  • the rotary valve 10 may also be configured such that the closing element 13 is not movable in the longitudinal direction L, so that the closing element 13 always rests against the valve seat 12 and can be rotated in this position with respect to the valve seat 12 in the direction of rotation D l or D2 to the Rotary slide valve 10 to open positively controlled by turning
  • FIG. 7 schematically shows the activation of a reciprocating piston engine 2.
  • the reciprocating piston engine 2 according to the invention comprises, as already described in FIGS. 1 a and 1 b, a cylinder 3 and a cylinder 3 therein
  • the reciprocating engine 2 comprises a controllable first valve
  • the drive device 100 is signal conductively connected to the first valve 6 and the second valve 7, for example by an electrical line 100a for driving the drive 15, a line 100b for detecting the position of the
  • the drive device 100 controls the second valve 7 in such a way that it is forcibly closed before the top dead center P3, that is, as shown in FIG. 3, at point P2, by a residual gas quantity GR in the working space 5 up to the top dead center P3 To compress, and thereby reduce the voltage applied to the first valve 6 in the region of the top dead center P3 pressure difference, so advantageously applied to the first valve 6 little or no pressure difference, in a particularly advantageous embodiment, the pressure in the interior 5 is higher than in the pressure vessel 9, so that the closing element 13 in
  • Figure 15 shows schematically a reciprocating engine 2 comprising a cylinder 3, a double-acting piston 4 and a first
  • a fluid inlet 21a is fluidly connected to the first interior 5a via a fluid line 21 and a free-flowing first valve 6a.
  • the first interior 5a is fluid-conductively connected to the fluid outlet 21b via a freely running second valve 7a and a fluid line 21.
  • the second valve 7a or the fluid line 21 is fluid via a fluid line 21c and via a controllable rotary valve 6b with the second
  • the second inner space 5b is above a
  • the rotary slide valves 6b and 7b each comprising a valve seat 12 and a closing element 13, are connected via a signal line 100a to a drive device, not shown.
  • the arrangement shown in FIG. 15 makes it possible to control the amount of fluid delivered between inlet 21a and outlet 21b in a range between 0% and 100%.
  • the amount of fluid delivered is 100% if the
  • controllable rotary valves 6b, 7b are controlled as if they were free-running valves, wherein the valve 6b would be an outlet valve and the valve 7b an inlet valve.
  • the rotary slide valves 6b, 7b are controlled in such a way that at least a part of the conveyed fluid is circulated in the fluid direction u by the fluid exiting via the second valve 7a partially or even completely via the fluid line 21c and the
  • Rotary slide valve 6b is supplied to the second inner space 5b, and in which the located in the second inner space 5b fluid over
  • Rotary slide valve 7b and the fluid line 21c and the first valve 6a is again supplied to the first inner space 5a.
  • the rotary slide valves 6b, 7b are controlled such that the entire contents of the first interior 5a is supplied to the second inner space 5b, and then by the entire contents of the second Interior 5b is again supplied to the first interior 5a, so that no fluid or a negligible amount of fluid is conveyed through the fluid inlet 21a and the fluid outlet 21b.
  • the rotary valve valves 6b, 7b it is possible to vary the delivery rate of the fluid between the inlet 21a and the outlet 21b in a range of 0 to 100%.
  • the method described with reference to FIG. 15 could also be operated with two single-acting pistons 4, so that two cylinders 3 with pistons 4 would be required for operation.
  • FIG. 16 schematically shows a further embodiment of a
  • Reciprocating engine 2 comprising a machine housing 2a, a common shaft 2b and a plurality of attached to the machine housing 2a cylinders 3, the pistons 4 are driven via a respective piston rod 2c of the common shaft 2b.
  • the reciprocating engine 2 comprises four cylinders 3c, 3d, 3e, 3f, wherein the fluid-conducting connections and the valves are not shown in detail.
  • Figure 17 shows schematically and by way of example, a possible fluid-conducting Verschal device of the reciprocating piston engine 2 shown in Figure 16, and fluid lines 21 and a first, a second and a third cooler 22a, 22b, 22c.
  • the four cylinders 3 c, 3 d, 3 e, 3 f are operated such that the first cylinder 3 c, the second cylinder 3 d and the third cylinder 3 e operated as a compressor wherein each cylinder outlet is fed via a fluid line 21 to a subsequent cooler 22a, 22b, 22c, and that the fourth cylinder 3f is operated as an expander, wherein a fluid to be processed is supplied to a fluid inlet 21a and is discharged from the fluid outlet 21b after expansion.
  • a Reciprocating piston 2 may have a plurality of pistons 4 and 3 cylinder, at least two, these cylinders 3 are operated as a compressor or as an expander depending on the particular control. Since all pistons 4 are driven by a common crankshaft 2b, there is the advantage that the piston operated by the expander as an expander can be fed directly via the crankshaft 2 to the piston 4 operated by the common crankshaft 2.
  • the arrangement shown also has the advantage that each of the cylinder 3 can be operated either as a compressor or as an expander by a corresponding control of the valves, preferably for each cylinder 3 individually and independently of the other cylinders can be determined, whether this as a compressor or operated as an expander.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un procédé d'expansion d'un gaz de pression sous une pression de gaz (pD) avec un moteur à pistons alternatifs par compression d'une quantité résiduelle de gaz et ouverture d'une première soupape au point mort supérieur (P3), en ce que le gaz sous pression pénètre dans une chambre de travail du moteur à pistons alternatifs lorsque la première soupape est ouverte et la première soupape est ensuite fermée au point (P4), le gaz est détendu jusqu'au point mort inférieur (P1), le gaz détendu est partiellement éjecté de l'espace de travail, et l'espace de travail est fermé avant d'atteindre le point mort supérieur (P3) du moteur à pistons alternatifs afin que la quantité résiduelle de gaz dans l'espace de travail après fermeture soit comprimée au point mort supérieur (P3).
PCT/EP2018/068724 2017-07-10 2018-07-10 Procédé et dispositif d'expansion d'un gaz avec un moteur à pistons alternatifs Ceased WO2019011951A1 (fr)

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EP17180429.7 2017-07-10

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PCT/EP2018/068724 Ceased WO2019011951A1 (fr) 2017-07-10 2018-07-10 Procédé et dispositif d'expansion d'un gaz avec un moteur à pistons alternatifs
PCT/EP2018/068723 Ceased WO2019011950A1 (fr) 2017-07-10 2018-07-10 Procédé et dispositif pour détendre un gaz au moyen d'un moteur à piston

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US (1) US11519267B2 (fr)
EP (1) EP3652417B1 (fr)
JP (1) JP7225196B2 (fr)
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CN113074098B (zh) * 2021-03-30 2023-01-10 北京建筑大学 一种活塞式膨胀压缩机及其应用方法和系统

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WO2001059266A1 (fr) 2000-02-07 2001-08-16 Compart Compressor Technology Gmbh & Co. Kg Dispositif et procede de commande d'une machine a piston
WO2009074800A1 (fr) * 2007-12-11 2009-06-18 Isentropic Limited Vanne
US20130032743A1 (en) * 2011-07-19 2013-02-07 Lightsail Energy Inc. Valve
US20130152568A1 (en) * 2011-12-16 2013-06-20 Jeffrey Modderno Valve activation in compressed-gas energy storage and recovery systems

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JPS5877111A (ja) * 1981-11-02 1983-05-10 Komatsu Ltd エンジンの吸・排気弁開閉時期操作装置
DE59100064D1 (de) * 1990-05-04 1993-04-29 Wolfgang Barth Verfahren zum antrieb eines pneumatischen motors und vorrichtung zur durchfuehrung des verfahrens.
WO2009050215A2 (fr) * 2007-10-18 2009-04-23 Burckhardt Compression Ag Soupape à commande active, et procédé pour faire fonctionner une soupape à commande active
CN102472265B (zh) * 2009-07-23 2015-07-01 伯克哈特压缩机股份公司 供给量控制方法和具有供给量控制功能的往复活塞式压缩机
AT509394B1 (de) * 2010-02-05 2012-01-15 Man Nutzfahrzeuge Oesterreich Verfahren zum betrieb eines kolbenexpanders eines dampfmotors
JP2011256800A (ja) * 2010-06-10 2011-12-22 Panasonic Corp 気体機械及びそれを用いる車両及び気体機械の駆動方法
GB201012743D0 (en) 2010-07-29 2010-09-15 Isentropic Ltd Valves
US20120297772A1 (en) * 2011-05-17 2012-11-29 Mcbride Troy O Systems and methods for efficient two-phase heat transfer in compressed-air energy storage systems
ITMI20112393A1 (it) * 2011-12-27 2013-06-28 Nuovo Pignone Spa Valvole rotative attuate roto-traslanti per compressori alternativi e relativi metodi
ITCO20120022A1 (it) * 2012-05-02 2013-11-03 Nuovo Pignone Srl Valvole rotative per compressori alternativi e relativi metodi

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
WO2001059266A1 (fr) 2000-02-07 2001-08-16 Compart Compressor Technology Gmbh & Co. Kg Dispositif et procede de commande d'une machine a piston
WO2009074800A1 (fr) * 2007-12-11 2009-06-18 Isentropic Limited Vanne
US20130032743A1 (en) * 2011-07-19 2013-02-07 Lightsail Energy Inc. Valve
US20130152568A1 (en) * 2011-12-16 2013-06-20 Jeffrey Modderno Valve activation in compressed-gas energy storage and recovery systems

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WO2019011950A1 (fr) 2019-01-17
US20200166036A1 (en) 2020-05-28
CN110892135A (zh) 2020-03-17
CN110892135B (zh) 2022-04-05
JP2020526702A (ja) 2020-08-31
KR20200023472A (ko) 2020-03-04
EP3652417B1 (fr) 2022-12-28
KR102638478B1 (ko) 2024-02-19
JP7225196B2 (ja) 2023-02-20
EP3652417A1 (fr) 2020-05-20
US11519267B2 (en) 2022-12-06

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